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EP2083165A1 - Buse à injection - Google Patents

Buse à injection Download PDF

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Publication number
EP2083165A1
EP2083165A1 EP08001566A EP08001566A EP2083165A1 EP 2083165 A1 EP2083165 A1 EP 2083165A1 EP 08001566 A EP08001566 A EP 08001566A EP 08001566 A EP08001566 A EP 08001566A EP 2083165 A1 EP2083165 A1 EP 2083165A1
Authority
EP
European Patent Office
Prior art keywords
valve needle
bore
injection nozzle
region
transition
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP08001566A
Other languages
German (de)
English (en)
Inventor
Ricardo Pimenta
Malcolm Lambert
Andy Limmer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Delphi Technologies Inc
Original Assignee
Delphi Technologies Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Delphi Technologies Inc filed Critical Delphi Technologies Inc
Priority to EP08001566A priority Critical patent/EP2083165A1/fr
Priority to PCT/EP2009/050554 priority patent/WO2009092690A1/fr
Publication of EP2083165A1 publication Critical patent/EP2083165A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/12—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship providing a continuous cyclic delivery with variable pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1886—Details of valve seats not covered by groups F02M61/1866 - F02M61/188
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus

Definitions

  • the present invention relates to an injection nozzle for use in a fuel injection system for an internal combustion engine. It relates particularly, but not exclusively, to an injection nozzle for use in a common rail fuel injection system for an internal combustion engine.
  • Each injector includes an injection nozzle having a valve needle which is operated by means of an actuator to move towards and away from a valve seating so as to control fuel delivery by the injector.
  • FIG. 1 is a part-perspective view of a conventional injection nozzle.
  • the injection nozzle 10 comprises a nozzle body 12 and a valve needle 14.
  • the valve needle 14 is shown in perspective and the nozzle body 12 is shown in cross-section.
  • the nozzle body 12 is provided with a blind bore 16 within which the valve needle 14 is movable to engage with, and disengage from, a valve needle seating 18 defined by the blind end of the bore 16.
  • the nozzle body 12 also includes a set of nozzle outlets 20 through which fuel can be injected into the associated engine cylinder or combustion space, in circumstances in which the valve needle 14 is lifted from its seating 18.
  • the blind end of the bore 16 defines a sac volume 22 with which inlet ends of the nozzle outlets 20 communicate.
  • the valve needle 14 has a generally circular cross-section along it's primary axis, and is divided into a plurality of regions which are shaped so as to optimise the flow of fuel from the injection nozzle 10 to the associated engine cylinder.
  • the valve needle 14 comprises a guide region 24 for guiding the valve needle 14 as it moves within the nozzle body 12.
  • the guide region 24 is formed from a generally cylindrical region into which there are machined a plurality of flat portions 24a.
  • Figure 2 is a sectional view of the injection nozzle of Figure 1 along the line B-B.
  • the guide region 24 comprises three flat portions 24a. Each of the flat portions 24a, are separated by a corresponding guide portion 24b in the circumferential direction of the guide region 24.
  • each of the guide portions 24b is sized so as to be a close clearance fit with the surface of the bore 16, i.e. typically -0.015mm. Accordingly, the proximity of each guide portion 24b to the surface of the bore 16 ensures the movement of the valve needle 14 toward and away from the valve seating 18 is co-axial with the primary axis of the bore 16, labelled A-A in Figure 1 .
  • Each flat portion 24a of the guide region 24 defines a corresponding relieved region 26 between the surface of the guide region 24 and the adjacent surface of the bore 16.
  • the purpose of the flat portions 24a is to allow sufficient fuel to flow from an upper inlet end of the injection nozzle 10, past the guide region 24, and toward the valve seating 18 disposed at the lower end of the injection nozzle 10.
  • an injection nozzle for a compression-ignition internal combustion engine comprising:
  • the accurate control of the injection of a small amount of fuel is possible at low needle lifts, since the restriction between the shoulder portion and the transition prevents excessive fuel from flowing through the nozzle. Furthermore, the restriction enables more accurate valve needle control, by causing a reduction in the fuel pressure downstream of the restriction at low needle lifts, and a corresponding reduction in the opening force exerted on the valve needle, thereby providing a damping effect which reduces the speed at which the valve needle lifts.
  • the relieved region comprises a first flat portion and a first tapered portion, disposed between the first flat portion and the shoulder portion.
  • the first flat portion is adjacent to the transition between the first and second bore regions when the valve needle is in a full lift state. Accordingly, when the valve needle is in the full lift state, the restriction to the flow of fuel between the first flat portion and the transition is less than the restriction defined between the transition and the shoulder portion. Thus, when the valve needle is at full lift the restriction to the flow of fuel is reduced such that the efficiency of the injection nozzle is not compromised at higher pressures and higher flows.
  • the first tapered portion is adjacent to the transition between the first and second bore regions when the valve needle is between a zero lift state and a full lift state.
  • the relieved region comprises a second flat portion and second tapered portion disposed between the second flat portion and the shoulder portion, wherein the second flat portion and the second tapered portion are spaced circumferentially around the valve needle from the first flat portion and the first tapered portion.
  • first flat portion and the first tapered portion are disposed on opposed sides of the valve needle from the second flat portion and the second tapered portion.
  • the injection nozzle of the present invention is of the type suitable for implementation within an injector having a piezoelectric actuator for controlling movement of an injection nozzle valve needle.
  • the injector is typically of the type used in common rail fuel injection systems for internal combustion engines (for example compression-ignition diesel engines).
  • Embodiments of an injection nozzle according to the present invention can be used in direct-acting piezoelectric injectors, where the piezoelectric actuator controls movement of the valve needle through a direct action, either via a hydraulic or mechanical amplifier or coupler, or by means of a direct connection.
  • Embodiments of an injection nozzle according to the present invention may also be used in injection systems which rely on the balance of spring and hydraulic forces to determine the valve needle actuation.
  • the injection nozzle 30, comprises a nozzle body 32 and a valve needle 34.
  • the nozzle body 32 is provided with a blind bore 35 within which the valve needle 34 is movable to engage with, and disengage from, a valve needle seating 38 defined by the blind end of the bore 35.
  • the valve seating 38 is of substantially frusto-conical form, as is known in the art.
  • the valve needle 34 terminates in valve tip 40, which has a generally conical shape.
  • the nozzle body 32 also includes a set of nozzle outlets (not shown) through which fuel can be injected into the associated engine cylinder or combustion space, in circumstances in which the valve needle 34 is lifted from its seating 38.
  • the blind end of the bore 35 defines a sac volume 42 with which inlet ends of the nozzle outlets communicate.
  • the valve needle 34 also includes a guide region 44 for guiding the valve needle 34 as it moves within the nozzle body 32 so as to ensure that the movement of the valve needle 34 is co-axial with the primary axis of the injection nozzle 30 A-A.
  • the guide region 44 is disposed between the valve tip 40 and the opposite end of the valve needle 34, where the valve needle 34 is coupled to an actuator (not shown). The guide region 44 will now be described in more detail with reference to Figures 4 and 5 .
  • the guide region 44 is formed from a generally cylindrical region which includes first and second flat portions 46a, 46b.
  • the flat portions 46a, 46b are disposed on opposed sides of the primary axis of the valve needle 34 and may be formed by machining the surface of the guide region 44.
  • the first and second flat portions 46a, 46b are separated from one another, in the circumferential direction of the valve needle 34, by first and second radiussed portions 47a, 47b as shown in Figure 5 .
  • the first and second radiussed portions 47a, 47b are sized so as to be a close clearance fit with the adjacent surface of the bore 35 of the nozzle body 32.
  • the bore 35 comprises first and second regions 36, 37, the second bore region 37 having a smaller diameter than the first bore region 36 and being disposed adjacent to the first bore region 36 in the axial direction of the injection nozzle 30.
  • the second bore region 37 is disposed adjacent to the guide region 44 of the valve needle 34.
  • the clearance between the radiussed portions 47a, 47b and the second bore region 37 is 0.015mm.
  • the first flat portion 46a is spaced from the surface of the second bore 37 so as to define a first transition volume 50a therebetween.
  • the spacing between the first flat portion 46a and the second bore region 37 is 0.675mm.
  • the first flat portion 46a terminates at its upper end in a first tapered portion 52a.
  • the radius of the valve needle 34 increases across the first tapered portion 50a in the upstream direction, and terminates at a shoulder portion 54 at the upper end of the guide region 44.
  • the shoulder portion 54 of the guide region 44 has a substantially circular cross-section and is a close clearance fit with the second bore region 37 around the entire circumference of the valve needle 34 in the region of the transition edge 48, when the valve needle 34 is in a zero lift position as shown in Figure 4 .
  • the second flat portion 46b is of the same configuration as the first flat portion 46a and defines a second transition volume 50b with the second bore region 37.
  • a second tapered portion 52b is provided between the upper end of the second flat portion 46b and the shoulder portion 54.
  • the shoulder 54 portion of the guide region 44 is disposed adjacent to the second bore region 37 and below the transition edge 48.
  • the length of the overlap in the axial direction of the injection nozzle 30 between the shoulder portion 54 and the second bore region 37 is labelled 'lift 1'.
  • lift 1 is 0.03mm.
  • the gap between the shoulder portion 54 and the second bore region 37 is 0.015mm. In this position, the flow area is equivalent to a hole with a diameter of 0.49mm. Accordingly, the flow of fuel from the entry volume 49 toward the sac volume 42 is substantially restricted.
  • valve needle 34 when the valve needle 34 is in the zero lift state, this corresponds to a non-injecting state of the injection nozzle 30. In this state, the valve tip 40 is engaged with the valve seating 38 of the nozzle body 32 and, accordingly, fuel is prevented from being injected into the associated engine cylinder.
  • the upper end of the valve needle 34 is coupled an actuator, such as a piezoelectric actuator, which is operable to lift the valve needle 34 so as to disengage from the valve seating 38 such that fuel is injected into the associated engine cylinder.
  • an actuator such as a piezoelectric actuator
  • the valve tip 40 is raised from the valve seating 38, allowing fuel to flow into the sac volume 42 and be injected into the associated cylinder.
  • a height of lift i.e. 0.03mm
  • the gap between the shoulder portion 54 and the second bore region 37 is a constant 0.015mm.
  • the flow of fuel from the entry volume 49 of the injection nozzle 30 through to the transition volume 50a, 50b and down to the sac volume 42 is restricted.
  • an excessive amount of fuel is prevented from being injected at a low needle lift.
  • the pressure in the nozzle downstream of the restriction i.e. in the transition volume 50a, 50b and the sac volume 42, reduces more rapidly as fuel exits the nozzle through the nozzle outlets. Accordingly, the opening force exerted on the valve needle 34 is reduced and, therefore, the speed with which the valve needle 34 lifts is also reduced. This effect is reversed when the valve needle 34 is closed.
  • valve needle 34 can be closed more quickly .
  • damping effect set up helps to control the valve needle 34 for small deliveries.
  • the restriction between the second bore region 37 and the guide region 44 of the valve needle 34 is defined by the transition edge 48 and the first and second flat portions 46a, 46b.
  • full lift of the valve needle 34 is a height of 0.3mm, although this could vary between 0.25mm and 0.4mm.
  • the width of the restriction is 0.675mm, i.e. the depth of the flat portions 46a, 46b.
  • the flow area is 2.8mm 2 which is equivalent to a hole with a diameter of 1.89mm.
  • the above described embodiment thus provides an injection nozzle in which fuel flow therethrough is substantially restricted at low needle lifts, thereby allowing the accurate injection of small quantities of fuel. Conversely, at high needle lifts, the restriction to the flow of fuel is reduced such that the efficiency of the injection nozzle is not compromised at higher pressures and higher flows.
  • first and second flat portions 46a, 46b, and the angle of the tapered portions 52a, 52b may be varied in order to obtain the optimal compromise between control of fuel flow at small needle lifts and increased fuel flow at large needle lifts.
  • the guide region 44 comprises first and second flat portions 46a, 46b which, together with the first and second tapered portions 52a, 52b, define a pair of relieved portions of the guide region 44.
  • the guide region 44 may be provided with only a single flat portion, and a corresponding tapered portion.
  • the guide portion 44 may be provided with more than two flat portions and a corresponding number of tapered portions spaced circumferentially around the valve needle 34.
  • the flat portions 46a, 46b and the tapered portions 52a, 52b of the guide region 44 may be created by machining the surface of a cylindrical guide region.
  • the advantages of the present invention i.e. accurate control of small quantity fuel injection, may be obtained without requiring additional manufacturing steps or substantial redesign of the known injection nozzle shown in Figures 1 and 2 .

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP08001566A 2008-01-22 2008-01-22 Buse à injection Withdrawn EP2083165A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP08001566A EP2083165A1 (fr) 2008-01-22 2008-01-22 Buse à injection
PCT/EP2009/050554 WO2009092690A1 (fr) 2008-01-22 2009-01-19 Injecteur de carburant

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP08001566A EP2083165A1 (fr) 2008-01-22 2008-01-22 Buse à injection

Publications (1)

Publication Number Publication Date
EP2083165A1 true EP2083165A1 (fr) 2009-07-29

Family

ID=39560566

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08001566A Withdrawn EP2083165A1 (fr) 2008-01-22 2008-01-22 Buse à injection

Country Status (2)

Country Link
EP (1) EP2083165A1 (fr)
WO (1) WO2009092690A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2722518A1 (fr) * 2012-10-22 2014-04-23 Delphi International Operations Luxembourg S.à r.l. Buse d'injection de carburant avec un élément de réduction d'écoulement
WO2017059986A1 (fr) * 2015-10-07 2017-04-13 Robert Bosch Gmbh Ensemble buse pour un injecteur de carburant et injecteur de carburant

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60132065A (ja) * 1983-12-20 1985-07-13 Nissan Motor Co Ltd 燃料噴射ノズル
US4987887A (en) * 1990-03-28 1991-01-29 Stanadyne Automotive Corp. Fuel injector method and apparatus
US5769319A (en) * 1995-01-23 1998-06-23 Cummins Engine Company, Inc. Injection rate shaping nozzle assembly for a fuel injector
DE19857244A1 (de) * 1998-12-11 2000-06-15 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
WO2002048536A1 (fr) * 2000-12-16 2002-06-20 Robert Bosch Gmbh Soupape d'injection de carburant destinee a des moteurs a combustion interne
WO2005116441A1 (fr) * 2004-05-26 2005-12-08 Robert Bosch Gmbh Soupape d'injection de carburant pour un moteur a combustion interne

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60132065A (ja) * 1983-12-20 1985-07-13 Nissan Motor Co Ltd 燃料噴射ノズル
US4987887A (en) * 1990-03-28 1991-01-29 Stanadyne Automotive Corp. Fuel injector method and apparatus
US5769319A (en) * 1995-01-23 1998-06-23 Cummins Engine Company, Inc. Injection rate shaping nozzle assembly for a fuel injector
DE19857244A1 (de) * 1998-12-11 2000-06-15 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
WO2002048536A1 (fr) * 2000-12-16 2002-06-20 Robert Bosch Gmbh Soupape d'injection de carburant destinee a des moteurs a combustion interne
WO2005116441A1 (fr) * 2004-05-26 2005-12-08 Robert Bosch Gmbh Soupape d'injection de carburant pour un moteur a combustion interne

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2722518A1 (fr) * 2012-10-22 2014-04-23 Delphi International Operations Luxembourg S.à r.l. Buse d'injection de carburant avec un élément de réduction d'écoulement
WO2014063907A1 (fr) * 2012-10-22 2014-05-01 Delphi International Operations Luxembourg S.À.R.L. Buse d'injection de combustible qui comprend un élément de limitation d'écoulement
JP2015532390A (ja) * 2012-10-22 2015-11-09 デルファイ・インターナショナル・オペレーションズ・ルクセンブルク・エス・アー・エール・エル 流れ制限要素を有する燃料噴射ノズル
WO2017059986A1 (fr) * 2015-10-07 2017-04-13 Robert Bosch Gmbh Ensemble buse pour un injecteur de carburant et injecteur de carburant

Also Published As

Publication number Publication date
WO2009092690A1 (fr) 2009-07-30

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